US3811291A - Method of operating a refrigeration plant and a plant for performing the method - Google Patents

Method of operating a refrigeration plant and a plant for performing the method Download PDF

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Publication number
US3811291A
US3811291A US00314993A US31499372A US3811291A US 3811291 A US3811291 A US 3811291A US 00314993 A US00314993 A US 00314993A US 31499372 A US31499372 A US 31499372A US 3811291 A US3811291 A US 3811291A
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United States
Prior art keywords
compressor
temperature
oil separator
liquid refrigerant
oil
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US00314993A
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English (en)
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L Schibbye
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Svenska Rotor Maskiner AB
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Svenska Rotor Maskiner AB
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B1/00—Compression machines, plants or systems with non-reversible cycle
    • F25B1/04—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type
    • F25B1/047—Compression machines, plants or systems with non-reversible cycle with compressor of rotary type of screw type
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
    • F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
    • F04C29/04—Heating; Cooling; Heat insulation
    • F04C29/042—Heating; Cooling; Heat insulation by injecting a fluid
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B31/00—Compressor arrangements
    • F25B31/006—Cooling of compressor or motor
    • F25B31/008—Cooling of compressor or motor by injecting a liquid

Definitions

  • the plant comprises means to introduce liquid refrigerant to the compression phase of the cycle ahead of the oil separator,
  • the plant further comprises means to adjust the amount of liquid refrigerant introduced in response to the temperature difference between the condenser and the oil separator, in order tokeep the difference on a constant level of 5C to 15C.
  • the present invention relates to refrigeration plants comprising a refrigerant flow circuit including a compressor of the screw rotor type, a condenser and an evaporator and more praticularly to such plants which also include means for circulating oil and for passing said oil through the compressor and having an oil separator provided in said circuit between the outlet of the compressor and the inlet of the condenser.
  • the oil is injected into the compression chambers of the compressor in order to cool thegaseous refrigerant during the compression and to seal the clearances at the intermesh between the rotors and at the periphery and end planesof the rotors. Further. in compressors having nonsynchronized rotors the oil also serves to lubricate the rotors.
  • liquid refrigerant As a cooling agent by introducing it into the com pressor of a refrigeration plant.
  • Some of these known proposals represent attempts to attain the desired cooling of the compressed gas without using oil while other are intended to solve specific problems in the operation of certain types of refrigerant compressors.
  • liquid refrigerant has very poor sealing and lubricating properties and therefore the replacement of oil by liq uid refrigerant in screw rotor compressors has not been successful.
  • the invention has for its object to provide a refrigeration plant of the type described in the introductory paragraph of this specification and further comprising means for introducing liquid refrigerant into a circuit portion between the inlet of the compressor and the inlet of the oil cooler, and a method of operating such a plant.
  • the introduction of the liquid refrigerant is controlled such that the temperature in the oil separator is kept at a level only slightly above the liquefaction temperature of the refrigerant at the pressure prevailing in the oil separator but is prevented from falling to said liquefaction temperature.
  • the invention makes it possible to attain a desired low oil temperature without the use of a separate oil cooler while obviating the risk of condensing of the gaseous refrigerant'within the-oil separator.
  • FIG. 1 diagrammatically illustrates an embodiment of a refrigeration plant according to the invention
  • FIG.2 is a detailed view of operating means included in the plant according to FIG. 1,
  • FIG. 3 is a modification of FIG. 1 and FIG. 4 is a further modification of the invention.
  • the compressor 10 may be of substantially the same type as shown in US. Pat. No. 3,432,089.
  • oil from a supply conduit 22 is injected into the compression chambers of the compressor for sealing and cooling purposes and leaves the compressor together with the vapourous refrigerant through a conduit 24 leading to an oil separator 26 of suitable type.
  • the oil-free high pressure refrigerant vapour flows through a conduit 28 to the condenser 12 where it condenses while the oil is removed from the oil separator 26 by a pump 30 and delivered to the conduit 22 which forms the discharge conduit of the pump.
  • the compressor '10 there is provided at least one noz zle which is connected to said conduit 32 and located such as to inject liquid refrigerant into the compression chambers of the compressor before the pressure in said chambers has reached the dis-- against the pressure prevailing in said chambers during this stage of the compression.
  • a metering valve 33 adjustable by means of an operating device 34.
  • This device 34 is controlled by a thermocouple having one joint 35 located at the inlet of the oil separator 26 and exposed to the temperature of the compressed fluid entering the separator and a second joint 36 located within the condenser 12.
  • the operating device 34 contains means for transforming the current produced by .the thermocouple into adjustment forces for actuating the valve 33 such that at increasing temperature difference between the joints 35 and 36 the valve 33 is actuated in an opening direction and at decreasing temper ature difference in a closing direction. In this manner it is possible to maintain the temperature difference substantially constant and at a value of about for instance to l5C.
  • the temperature in the oil separator 26 is slightly higher so that no liquefaction can take place in the separator. Further, the temperature of the oil leaving the separator through the conduit 22 is also always only slightly higher than the condensing temperature resulting in the best possible cooling effect when the oil is injected into the compressor.
  • the capacity of the compressor is variable by means of a slide valve as described in US. Pat. No. 3.432.089, so that the temperature in the refrigerating chamber 16 may automatically be kept substantially constant ina known manner.
  • the slide valve is adjustable by means of a hydraulic servomotor 38.
  • the slide valve is moved to decrease the capacity of the compressor.
  • This reduction of the capacity involves a reduction of the compression work and consequently also of the demand for cooling.
  • the speed of the oil pump 30 is not changed and therefore the injected oil quantity remains unchanged.
  • the counter pressure in the compressor at the'condensate injection point is lower than the pressure at full capacity and therefore the injected condensate quantity is at first increased.
  • the discharge temperature of the compressor will at firstdecrease before the pressure in the high pressure portion of the cirquit has assumed the somewhat lower value which will be the result of the reduced capacity of the compressor. It is evident that in this way there is a risk that the temperature in the oil separator 26 may temporarily sink down to the condensing-temperature.
  • the cam 42 may be shaped such that for each position of the slide valve the cam determines a preliminary specific setting of the metering valve 33 in which the supply of condensate to the compressor is sufficient to keep the temperature of the compressed gas at a level higher than the liquefaction or condensing temperature of the gaseous refrigerant at the pressure prevailing in the high pressure portion of the circuit when the plant operates under steady state condition at the actual position of the slide valve.
  • thermocouple 35 36 and the operating device 34 ascertain that the temperature in the oil separator 26 is only 5 to 15C higher than the condensing temperature.
  • the operating device 34 is shown in detail but diagramatically in FIG. 2.
  • the two conduits from the thermocouple 35, 36 are connected to a control device 52 which is adapted to supply current to an electric motor 54 to drive this motor in either direction in response to signals received from the thermocouple.
  • Th'eshaft 56 of the motor carries a worm 58 engaging a worm wheel 60 mounted on a shaft 62 perpendicular to the motor shaft 56.
  • a spur gear 64 which is drivingly connected to .the .worm wheel 60 via a slip coupling (not shown) and meshes with a rack 66.
  • This rack 66 is adapted to actuate the meteringvalve 33.
  • the cam follower 44 is provided with a head member 68 having a longitudinal slot 70 slidingly receiving'a pin 72 mounted at the lower end of the rack 66.
  • the cam 42 is shown in a position corresponding to full capacity of the compressor l0. ln this position the pin 72 is located at a small distance from the lowerend of the slot so that the rack 66 is free to move in the slot 70 in both directionsin response to. sig
  • thermocouple35 nals from the thermocouple35, '36 for fine adjustment of the meteringvalve 33 during the steady state condition.
  • the metering valve 33 is successively throttled so that the quantity of injected liquid refrigerant is decreased substantially in proportion to the decreasing compression work of the compressor. In this manner the temperature of the compressed fluid is prevented from falling down to the condensation temperature during the adjustment movement of the slide valve of the compressor.
  • the'slide valve is slowed down .and stopped and the thermocouple 35, 36 takes the control of metering valve 33 for fine adjustment of the temperature in the oil separator in relation to the temperature in the condenser.
  • the pin 72 is located near the lower end of the slot 70.
  • the slide valve When later on the temperature in the refrigerating chamber 16 tends to rise the slide valve is caused to move towards the full capacity position and the cam follower 44 is pulled downwardly. This downward movement takes place without the rack 66 being actuated because the slot 70 can move downwardly relatively to the pin 72. Therefore, the metering valve 33 remains in its partly throttled position until the thermocouple 35, 36 responds to the increasing temperature and causes the motor 54 to actuate the valve 33 in an opening direction.
  • FIG. 3 is illustrated a modification of the control device just described.
  • the liquid refrigerant is injected into the discharge conduit 24 of the compressor where the pressure is somewhat higher than the pressure in the condenser 12.
  • a pump 74 to which the liquid refrigerant from the condenser is. supplied through a conduit 32A.
  • the pump 74 is of the type having a non-return valve in its outlet and means for bypassing a variable liquid quantity which is returned to the condenser 12 through a conduit 76.
  • this conduit 76 is provided a valve 33A adapted to be operated'by a device similar to the device 34 described above. .However, in order to decrease the injected refrigerant quantity the valve 33A is actuated in an opening direction,
  • thermocouple 35, 36 since the liquefaction or condensing temperature of a gas varies with its p'ressure'the thermocouple 35, 36 maybe replaced by a temperature sensing device 80 and a pressure-sensing device 81 provided in the oil separator 26. These devices may be connected to a computer 82 adapted to produce a signal representing the difference between the temperature in the oil separator and the liquefaction temperature of the refrigerant at the pressure prevailing in the oil separator. this signal being used to control the supply of cooling liquid refrigerant.
  • a method of operating'a refrigeration plant comprising: a refrigerant flow circuit including a compressor of the screw rotor type, a condenser and an evapo rator; means for circulating oil and for injecting said oil into thecompression chambers of said compressor; an oil separator provided in said circuit between the outlet of said compressor and. the inlet of said condenser; and means for introducing liquid refrigerant into a circuit portion between the inlet of the compressor and the inlet of said oil separator;
  • a method asdefined in claim 1, comprising keeping the temperature in the oil separator at a temperature level which i's 5C to C higher than said liquefaction temperature.
  • a refrigeration plant comprising:
  • a refrigerant flow circuit including a compressor of the screw rotor type, a condenser and an evaporator;
  • a plant as defined in claim 3, comprising means for controlling the capacity of the compressor, said capacity controlling means being operatively connected to said adjustable means to reduce the quantity of liquid refrigerant introduced during operation at partial capacity.
  • said responsive means includes a temperature sensing device ineach of the condenser and the oil separator, said sensing devices being combined to produce a signal representing said temperature difference, said connecting means controlling said adjustable means as a function of said signal to keep said difference substantially constant.
  • said responsive means includes a temperature sensing device and a pressure sensing device coupled to said oil separator
  • said devices being connected to a computer for producing a signal representing the difference between ,the temperature in the oil separator and the liquefaction temperature of the refrigerant at the pressure'prevailing in the oil separator.
  • said adjustable means comprises a valve means coupled in the path of said liquid refrigerant to said compressor, said valve means being opened to increase the quantity of said liquid refrigerant introduced into said compressori.
  • a plant according to claim 3. wherein said liquid refrigerant is introduced into a discharge conduit of said compressor and including return conduit means returning liquid refrigerant to said condenser, said adjustable means comprising a valve means in said return conduit, said valve means being closed to increase the quantity of liquid refrigerant introduced into said discharge conduit of said compressor.
  • said connecting means comprises a motor coupled to said adjustable means via a gear mechanism, said capacity perature sensing and pressure sensing devices are in said oil separator.
  • a method as defined in claim 1 comprising controlling the introduction of said liquid refrigerant into the compression chambers of said compressor.
  • a method according to claim 1 comprising controlling the introduction of saidliquid refrigerantinto said compressor.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Applications Or Details Of Rotary Compressors (AREA)
US00314993A 1971-12-28 1972-12-14 Method of operating a refrigeration plant and a plant for performing the method Expired - Lifetime US3811291A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
GB6027471A GB1384397A (en) 1971-12-28 1971-12-28 Refrigeration plants

Related Child Applications (1)

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US06/082,422 Reissue USRE30869E (en) 1971-12-28 1979-10-05 Method of operating a refrigeration plant and a plant for performing the method

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US00314993A Expired - Lifetime US3811291A (en) 1971-12-28 1972-12-14 Method of operating a refrigeration plant and a plant for performing the method
US06/082,422 Expired - Lifetime USRE30869E (en) 1971-12-28 1979-10-05 Method of operating a refrigeration plant and a plant for performing the method

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US (2) US3811291A (ja)
JP (1) JPS5544862B2 (ja)
CA (1) CA974073A (ja)
CS (1) CS164220B2 (ja)
DD (1) DD102797A5 (ja)
DE (1) DE2261336C2 (ja)
DK (1) DK149937C (ja)
GB (1) GB1384397A (ja)
IN (1) IN138133B (ja)
IT (1) IT972677B (ja)
NL (1) NL176016C (ja)
SE (1) SE395314B (ja)

Cited By (21)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3874192A (en) * 1973-03-08 1975-04-01 Maekawa Seisakusho Kk Oil cooling apparatus for refrigerators
US3922873A (en) * 1974-11-14 1975-12-02 Carrier Corp High temperature heat recovery in refrigeration
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
US3990264A (en) * 1974-11-14 1976-11-09 Carrier Corporation Refrigeration heat recovery system
US4018583A (en) * 1975-07-28 1977-04-19 Carrier Corporation Refrigeration heat recovery system
US4020642A (en) * 1973-11-19 1977-05-03 Hall-Thermotank Products Limited Compression systems and compressors
US4112701A (en) * 1975-09-29 1978-09-12 Svenska Rotor Maskiner Aktiebolag Method and means for cooling the oil in a system including a compressor with oil supply, as well as such systems
USRE30252E (en) * 1974-11-14 1980-04-08 Carrier Corporation High temperature heat recovery in refrigeration
US4275570A (en) * 1980-06-16 1981-06-30 Vilter Manufacturing Corporation Oil cooling means for refrigeration screw compressor
US4497185A (en) * 1983-09-26 1985-02-05 Dunham-Bush, Inc. Oil atomizing compressor working fluid cooling system for gas/vapor/helical screw rotary compressors
US4558573A (en) * 1983-09-30 1985-12-17 Samifi Babcock, S.P.A. Device for oil cooling in a compression unit and, particularly, a screw compression unit
WO1986005576A1 (en) * 1985-03-22 1986-09-25 Svenska Rotor Maskiner Ab Method for refrigeration systems
US5168721A (en) * 1991-03-28 1992-12-08 K-Whit Tools, Inc. Refrigerant recovery device
US5222369A (en) * 1991-12-31 1993-06-29 K-Whit Tools, Inc. Refrigerant recovery device with vacuum operated check valve
US5317903A (en) * 1991-12-19 1994-06-07 K-Whit Tools, Inc. Refrigerant charging system controlled by charging pressure change rate
US5758506A (en) * 1996-07-03 1998-06-02 White Industries, Llc Method and apparatus for servicing automotive refrigeration systems
US6122924A (en) * 1999-06-30 2000-09-26 Carrier Corporation Hot gas compressor bypass using oil separator circuit
EP1400765A3 (en) * 2002-09-17 2005-09-28 Kabushiki Kaisha Kobe Seiko Sho Screw refrigerating apparatus
US20080078204A1 (en) * 2006-10-02 2008-04-03 Kirill Ignatiev Refrigeration system
US20080078192A1 (en) * 2006-10-02 2008-04-03 Kirill Ignatiev Injection system and method for refrigeration system compressor
WO2008042358A1 (en) * 2006-10-02 2008-04-10 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor

Families Citing this family (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3913346A (en) * 1974-05-30 1975-10-21 Dunham Bush Inc Liquid refrigerant injection system for hermetic electric motor driven helical screw compressor
JPS6361410U (ja) * 1986-10-09 1988-04-23
JPS6361409U (ja) * 1986-10-09 1988-04-23
BE1022707B1 (nl) * 2015-02-11 2016-08-19 Atlas Copco Airpower Naamloze Vennootschap Werkwijze en inrichting voor het regelen van de olietemperatuur van een oliegeïnjecteerde compressorinstallatie of vacuümpomp en klep toegepast in dergelijke inrichting

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US2739450A (en) * 1952-09-30 1956-03-27 Carrier Corp Refrigeration system provided with compressor unloading mechanism
US3062020A (en) * 1960-11-18 1962-11-06 Gen Motors Corp Refrigerating apparatus with compressor output modulating means
US3379033A (en) * 1966-08-10 1968-04-23 Vilter Manufacturing Corp Refrigeration system and apparatus
US3408826A (en) * 1967-01-27 1968-11-05 Dunham Bush Inc Refrigeration system and systems for cooling and controlling compressors
US3408828A (en) * 1967-09-08 1968-11-05 Dunham Bush Inc Refrigeration system and system for separating oil from compressed gas

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2776542A (en) * 1955-07-07 1957-01-08 Gen Electric Motor cooling means for hermetically sealed refrigerant compressor unit
US3165681A (en) * 1962-12-31 1965-01-12 Honeywell Inc Motor control apparatus employing a balanceable switching device
GB1287309A (en) 1970-10-29 1972-08-31 Kuehlautomat Veb Screw rotor compressor
US3791165A (en) * 1971-11-18 1974-02-12 Carrier Corp Charging method and apparatus for a refrigeration system

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US2739450A (en) * 1952-09-30 1956-03-27 Carrier Corp Refrigeration system provided with compressor unloading mechanism
US3062020A (en) * 1960-11-18 1962-11-06 Gen Motors Corp Refrigerating apparatus with compressor output modulating means
US3379033A (en) * 1966-08-10 1968-04-23 Vilter Manufacturing Corp Refrigeration system and apparatus
US3408826A (en) * 1967-01-27 1968-11-05 Dunham Bush Inc Refrigeration system and systems for cooling and controlling compressors
US3408828A (en) * 1967-09-08 1968-11-05 Dunham Bush Inc Refrigeration system and system for separating oil from compressed gas

Cited By (31)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3874192A (en) * 1973-03-08 1975-04-01 Maekawa Seisakusho Kk Oil cooling apparatus for refrigerators
US3945216A (en) * 1973-06-18 1976-03-23 Svenska Rotor Maskiner Aktiebolag Refrigeration systems
US4020642A (en) * 1973-11-19 1977-05-03 Hall-Thermotank Products Limited Compression systems and compressors
USRE30252E (en) * 1974-11-14 1980-04-08 Carrier Corporation High temperature heat recovery in refrigeration
US3922873A (en) * 1974-11-14 1975-12-02 Carrier Corp High temperature heat recovery in refrigeration
US3990264A (en) * 1974-11-14 1976-11-09 Carrier Corporation Refrigeration heat recovery system
US4018583A (en) * 1975-07-28 1977-04-19 Carrier Corporation Refrigeration heat recovery system
US4112701A (en) * 1975-09-29 1978-09-12 Svenska Rotor Maskiner Aktiebolag Method and means for cooling the oil in a system including a compressor with oil supply, as well as such systems
US4275570A (en) * 1980-06-16 1981-06-30 Vilter Manufacturing Corporation Oil cooling means for refrigeration screw compressor
US4497185A (en) * 1983-09-26 1985-02-05 Dunham-Bush, Inc. Oil atomizing compressor working fluid cooling system for gas/vapor/helical screw rotary compressors
US4558573A (en) * 1983-09-30 1985-12-17 Samifi Babcock, S.P.A. Device for oil cooling in a compression unit and, particularly, a screw compression unit
WO1986005576A1 (en) * 1985-03-22 1986-09-25 Svenska Rotor Maskiner Ab Method for refrigeration systems
US5168721A (en) * 1991-03-28 1992-12-08 K-Whit Tools, Inc. Refrigerant recovery device
US5335512A (en) * 1991-03-28 1994-08-09 K-Whit Tools, Inc. Refrigerant recovery device
US5317903A (en) * 1991-12-19 1994-06-07 K-Whit Tools, Inc. Refrigerant charging system controlled by charging pressure change rate
US5222369A (en) * 1991-12-31 1993-06-29 K-Whit Tools, Inc. Refrigerant recovery device with vacuum operated check valve
US5758506A (en) * 1996-07-03 1998-06-02 White Industries, Llc Method and apparatus for servicing automotive refrigeration systems
US6122924A (en) * 1999-06-30 2000-09-26 Carrier Corporation Hot gas compressor bypass using oil separator circuit
EP1400765A3 (en) * 2002-09-17 2005-09-28 Kabushiki Kaisha Kobe Seiko Sho Screw refrigerating apparatus
US7647790B2 (en) * 2006-10-02 2010-01-19 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor
US20080078192A1 (en) * 2006-10-02 2008-04-03 Kirill Ignatiev Injection system and method for refrigeration system compressor
WO2008042358A1 (en) * 2006-10-02 2008-04-10 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor
US20080236179A1 (en) * 2006-10-02 2008-10-02 Kirill Ignatiev Injection system and method for refrigeration system compressor
US20080078204A1 (en) * 2006-10-02 2008-04-03 Kirill Ignatiev Refrigeration system
US20100095704A1 (en) * 2006-10-02 2010-04-22 Kirill Ignatiev Injection System and Method for Refrigeration System Compressor
CN101523130B (zh) * 2006-10-02 2011-06-08 艾默生环境优化技术有限公司 用于制冷系统压缩机的喷射系统和方法
US8181478B2 (en) 2006-10-02 2012-05-22 Emerson Climate Technologies, Inc. Refrigeration system
CN102213498B (zh) * 2006-10-02 2013-01-30 艾默生环境优化技术有限公司 用于制冷系统压缩机的喷射系统和方法
CN102213499B (zh) * 2006-10-02 2013-02-06 艾默生环境优化技术有限公司 用于制冷系统压缩机的喷射系统和方法
CN102168895B (zh) * 2006-10-02 2013-03-20 艾默生环境优化技术有限公司 用于制冷系统压缩机的喷射系统和方法
US8769982B2 (en) 2006-10-02 2014-07-08 Emerson Climate Technologies, Inc. Injection system and method for refrigeration system compressor

Also Published As

Publication number Publication date
IT972677B (it) 1974-05-31
GB1384397A (en) 1975-02-19
CA974073A (en) 1975-09-09
JPS4873838A (ja) 1973-10-05
NL7217736A (ja) 1973-07-02
DD102797A5 (ja) 1973-12-20
JPS5544862B2 (ja) 1980-11-14
NL176016C (nl) 1985-02-01
CS164220B2 (ja) 1975-11-07
DK149937C (da) 1987-10-26
USRE30869E (en) 1982-02-23
DK149937B (da) 1986-10-27
DE2261336A1 (de) 1973-07-05
AU5011772A (en) 1974-06-20
NL176016B (nl) 1984-09-03
DE2261336C2 (de) 1985-05-09
SE395314B (sv) 1977-08-08
IN138133B (ja) 1975-12-20

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